GB2445094A - Hydraulic valve arrangement - Google Patents

Hydraulic valve arrangement Download PDF

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Publication number
GB2445094A
GB2445094A GB0724634A GB0724634A GB2445094A GB 2445094 A GB2445094 A GB 2445094A GB 0724634 A GB0724634 A GB 0724634A GB 0724634 A GB0724634 A GB 0724634A GB 2445094 A GB2445094 A GB 2445094A
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GB
United Kingdom
Prior art keywords
arrangement
valve
compensation
post
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
GB0724634A
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GB0724634D0 (en
Inventor
Thorkild Christensen
Siegfried Zenker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Danfoss Power Solutions ApS
Original Assignee
Sauer Danfoss ApS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sauer Danfoss ApS filed Critical Sauer Danfoss ApS
Publication of GB0724634D0 publication Critical patent/GB0724634D0/en
Publication of GB2445094A publication Critical patent/GB2445094A/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F15B2211/50527—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves using cross-pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/877—With flow control means for branched passages
    • Y10T137/87885—Sectional block structure

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

A hydraulic valve arrangement with several valve modules 2-6 each have a supply channel arrangement with a high-pressure channel 7 and a low-pressure channel 8, a work connection arrangement with at least one work connection A, B, a directional valve arrangement 15, 16 between the supply channel arrangement and the work connection arrangement and a compensation arrangement 19, 28. In order to improve the control possibilities, in at least one valve module 3, 5, the compensation arrangement is a pre-compensation arrangement 19 and, in at least one other valve module 4, 6, the compensation arrangement is a post-compensation arrangement 28.

Description

( 2445094 jydrau1ic valve arrangement The invention concerns a
hydraulic valve arrangement with several valve modules, each having a supply channel arrangement with a high-pressure channel and a lowpressure channel, a work connection arrangement with at least one work connection, a directional valve arrangement between the supply channel arrangement and the work connection arrangement, and a compensation arrangement.
Such a valve arrangement is used in many cases to actuate hydraulic drives in a work machine, a vehicle or another arrangement. For example in a backhoe, a first hydraulic drive can be used to tilt a beam in relation to a chassis, a second hydraulic drive can be used to tilt an arm in relation to the beam and a third hydraulic drive can be used to actuate a shovel. A fourth hydraulic drive can be provided to turn the upper vehicle body in relation to the lower vehicle body.
In this connection, the use of a compensation arrangement has the advantage that load-pressure independent control is obtained. The compensation arrangement ensures that the pressure drop across the directional valve arrangement or across a measuring orifice combined with the directional valve arrangement remains constant, independent of the intensity of the work pressure and independent of the opening degree of the directional valve arrangement. Thus, the flow of the hydraulic fluid from the supply channel arrangement to the connected hydraulic drive basically only depends on the opening degree of the directional ( valve arrangement. Thus, a practically proportional function of the directional valve arrangement is obtained.
In principle, there are two different ways of designing a compensation arrangement. A first compensation arrangement, in the following called "pre-compensation arrangement", has a compensation valve that is located upstream, as regards the technicalities of the flow, of the measuring orifice mentioned above. The compensation device has a throttle slide that is acted upon in the closing direction by the pressure upstream of the measuring orifice and in the opening direction by the pressure downstream of the measuring orifice, that is, by the load pressure plus the pressure of a spring. Such a compensation arrangement is occasionally also called a "primary individual compensation valve".
Another construction, in the following called a "post-compensation arrangement, uses a compensation valve that is connected in the flow direction downstream of the measuring orifice. The throttle slide in the downstream located compensation valve is acted upon in the opening direction of the pressure downstream of the measuring orifice and in the closing direction by the highest load pressure and a spring.
With a valve module with post-compensation arrangement, a parallel actuation of two or more valve modules and an insufficient supply of hydraulic fluid will cause a uniform reduced fluid flow via all measuring orifices. The available fluid flow will thus be distributed proportionally to all drives. This is not possible with a valve module with a pre-compensation arrangement. (
The invention is based on the problem of improving the control possibilities of a valve arrangement.
The present invention provides a hydraulic valve arrangement comprising a plurality of valve modules, each valve module having a supply channel arrangement comprising a high-pressure channel and a low-pressure channel, a work connection arrangement with at least one work connection, a directional valve arrangement between the supply channel arrangement and the work connection arrangement, and a compensation arrangement, wherein, in at least one valve module, the compensation arrangement is a pre-compensation arrangement and, in at least one other valve module, the compensation arrangement is a post-compensation arrangement.
With a hydraulic valve arrangement as mentioned in the introduction, the above-mentioned problem is solved in that in at least one valve module the compensation arrangement is a pre-compensation arrangement and in at least one other valve module the compensation arrangement is a post-compensation arrangement.
With this embodiment, during insufficient supply, the drive or the drives connected to the valve module or valve modules with pre-compensation arrangement can be controlled differently from the drives connected to valve modules with post-compensation arrangement. With the example mentioned above of a backhoe with several drives, the drive turning the upper vehicle body in relation to the lower vehicle body can, for example, be connected to a pre-compensated valve module, whereas the other drives
C
that actuate the shovel, the arm and the beam can be connected to post-compensated valve modules. If all drives are then actuated at the same time, an insufficient supply will probably occur. This insufficient supply will then be distributed differently from usual. The turning drive will practically not be affected by the insufficient supply.
The upper vehicle body will continue to turn at the speed wanted by the user. The remaining drives receive the rest of the hydraulic fluid, which will then be distributed proportionally to the individual positions of the directional valves. Many users find such control behaviour more comfortable, Of course, also other examples can be imagined, in which pre-compensated valve modules and post-compensated valve modules are mixed in a valve arrangement with several valve modules.
Preferably, the post-compensation arrangement has a closing spring and the pre-compensation arrangement has an opening spring, the closing spring being weaker than the opening spring. In the post-compensation arrangement, the closing spring acts together with the pressure in a load sensing line. The pressure behind the measuring orifice acts in the opening direction. With a pre-compensated valve, however, the spring acts in the opening direction, and the pressure before the measuring orifice acts in the closing direction. The mentioned dimensioning of the springs ensures in a simple manner that the pre-compensated valve module will always have priority over the post-compensated valve module or valve modules.
Preferably, the opening spring generates a control force, which is smaller than the pressure force during idling which acts against the opening spring. Thus, energy-saving C' behaviour of the pre-compensated valve module can be achieved. Particularly, if the pressure present in the high-pressure channel is reduced during idling by a variable displacement pump or another control device, the pre-compensated valve can close or at least throttle heavily to interrupt a possible volume flow.
Preferably, in the valve module with the pre-compensation arrangement, the compensation arrangement is located in a line that runs from an outlet to an inlet of the directional valve arrangement. The pre-compensation arrangement is thus physically located after the directional valve arrangement and thus also after the measuring orifice. When actuated, the directional valve arrangement then frees a flow path for hydraulic fluid from the high-pressure channel to the inlet of the pre-compensation arrangement.
It is preferred that both the pre-compensation arrangement and the post-compensation arrangement are located in lines running from an outlet to an inlet of the directional valve arrangement. Thus, the designs of a pre-compensated valve module and a post-compensated valve module can approach each other. The costs of manufacturing are reduced.
It is particularly preferred that the compensation arrangements are located in the same position in both valve modules with pre-compensation arrangements and in valve modules with post-compensation arrangements. This permits an even closer approach of the design correlation between the valve module with pre-compensation arrangement and the valve module with post-compensation arrangement.
C
In a particularly preferred embodiment it is provided that both the valve module with pre-compensation arrangement and the valve module with post-compensation arrangement have similar valve housings and that a spring of the pre-compensation arrangement is located at a different side of a slide from a spring of the post-compensation arrangement.
This keeps the costs of manufacturing a valve arrangement low, also if valve modules with different control behaviours are used. The same valve housings can be used for both pre-cornpensation and post-compensation These valve housings merely have to have a few more channels than would be required if the valve housings were only meant for one function. The superfluous channels can simply be closed with plugs. This is more cost effective than providing different valve housings for the two functjonalitjes A hydraulic valve arrangement in accordance with the invention will now be described, by way of example only, with reference to the single figure of the accompanying drawing which shows a schematic view of the hydraulic valve arrangement.
Referring to the accompanying drawing, a hydraulic valve arrangement 1 has several valve modules 2-6. The valve modules 2-6 are flanged together in a block. A high-pressure channel 7 and a low-pressure channel 8, forming the supply channel arrangement, are led through the block.
An inlet module 9 is flanged onto one side of the block of valve modules 2-6, and an end module is flanged onto the opposite end. The inlet module 9 has a pressure connection ( P that is connected to the high-pressure channel. The end module has a connection T that is connected to the low-pressure channel. The high-pressure channel P can be connected to a pump or another pressure source. The low-pressure connection T is connected to a tank or other container. Further, the inlet module 9 has a load-sensing connection LS, which carries the highest load pressure present in the valve modules 2-6. A corresponding load pressure channel 11 also extends through all valve modules 2-6. In the end module 10, it is connected to the low-pressure line 8. Two-way valves 12 form a cascade in the load sensing channel 11. They pass on the higher pressure at the inlets to their outlet, so that in the inlet module 9 the load pressure channel 11 carries the higher pressure present in all valve modules 2-6.
The load pressure channel 11 has a section in the form of a load-sensing line 13, which also extends through all valve modules 2-6.
In the inlet module 9 is provided an inlet compensation valve 14, which ensures that the pressure in the high-pressure channel 7 always exceeds the pressure in the load-sensing channel 13 by an at least substantially constant value.
The valve module 2 has a work connection A and a further connection T2. The work connection A can be supplied with pressurised hydraulic fluid, whereas the connection T2 can not. Accordingly, a single-acting hydraulic drive can be connected to the valve module 2, said drive merely serving the purpose of lifting a load. The hydraulic volume displaced from the hydraulic drive during lifting of the load can then be adopted and discharged by the valve module 2 via the T2-connection. During lowering of the load, hydraulic fluid can be replenished via the T2-connection.
Each of the other valve modules 3-6 has two work connections A, B, which can, as will be explained below, be pressurised in a controlled manner.
The valve modules 3 and 5 are designed in the same way.
Both have a directional valve 15 connected in series with a measuring orifice 16. The measuring orifice 16 can, of course, also be part of the directional valve 15.
Therefore, the combination of measuring orifice 16 and directional valve 1 is called a directional valve arrangement.
Via an inlet 17, the directional valve 15 is connected to the high-pressure channel 7. An outlet 18 of the directional valve arrangement 15, 16 leads to a compensation valve 19, which has a compensation slide 20 acted upon in the opening direction by an opening spring 27 and in the closing direction by the pressure in the high-pressure channel 7. Further, the ptessure at the outlet 18 of the directional valve arrangement 15, 16 acts in the opening direction, so that the compensation slide always adjusts so that the pressure across the measuring orifice 16 corresponds to the force of the opening spring 27.
Via a non-return valve 21 opening in the direction of the directional valve 15, the compensation valve 19 is connected to an inlet 22 of the directional valve 15, said ( inlet being connectible to one of the work connections A, B in dependence on the actuation of the directional valve 15. Non-return valves 23, 24, which can be opened, are located before the work connections A, B, said non-return valves enabling a drop-proof connection of the hydraulic machines.
As the compensation valve 19 is controlled by the pressure before the measuring orifice 16, it is called a pre-compensation valve. The valve modules 3, 5 can also be called "pre-compensated" valve modules.
The valve modules 4, 6 also have the same design. Also here, a directional valve 15 and a measuring orifice 16 are provided, which together form a directional valve arrangement. The inlet of the directional valve 15 is connected to the high-pressure channel 7.
To the outlet 18 of the directional valve arrangement 15, 16 is also connected a compensation valve 28, the compensation slide 25 of which is acted upon in the closing direction by a closing spring 26. In the closing direction, the pressure at the load-sensing connection LS also acts, which pressure is passed on to here via the load-sensing line 13. In the opening direction, the pressure at the outlet 18 of the directional valve arrangement 15, 16 acts upon the compensation slide 25.
The outlet of the.compensation valve 28 is connected to the inlet 22 of the directional valve 15. In dependence on its position, the directional valve 15 can connect this inlet 22 to one of the work connections A, B, non-return
I
-10 -valves 23, 24 that can be opened also being provided here to prevent leakage at the work connections A, B. As the compensation valve 28 is controlled by the pressure after the measuring orifice 16, it is called a "post-compensation valve". Accordingly, the valve modules 4, 6 are "post-compensated" valve modules.
The valve module 2 also has a pre-compensation valve 19.
A pre-compensated valve module 3, 5, whose directional valve arrangement 15, 16 can be called an LS-valve with primary, individual compensation valve, enables no supply-dependent distribution of the available flow of hydraulic fluid. when several such valve modules in parallel operation control their drives at the same time, the drive with the lowest load-pressure will be the first to be supplied with hydraulic fluid, whereas the remaining volume flow will be led to the other drives. In the end, this results in that, during an insufficient supply, the function of the drive with the smallest load will be maintained whereas another drive with a larger load will stop.
A post-compensated valve module 4, 6, however, permits the distribution of the flow of hydraulic fluid proportionally to the positions of the individual directional valve arrangements 15, 16. A post-compensated valve module can also be called an "LC valve".
The closing spring 26 in the post-compensated valve modules 4, 6 is weaker than the opening spring 27 in the pre-compensated valve modules 3, 5. In this way, it is
S
-11 -ensured that the pre-cornpensated valve modules 3, 5 always have priority over the post-compensated valve modules 4, 6.
Therefore, during insufficient supply the drives connected to the pre-compensated valve modules 3, 5 will be actuated first. The drives connected to the post-compensated valve modules 4, 6, however, reduce their work speed proportionally.
The proportional reduction of the volume flow with post-compensated valves is mainly caused by the drop of the "margin pressure" that reduces the opening force at the compensator, whereas nothing changes on the spring side.
With post-compensated valves this drop has an immediate effect, whereas with pre-compensated valves the effect does not occur until the "margin pressure" drops below the spring value of the opening spring.
Preferably, the opening spring 27 can be made so that the pressure it provides is smaller than an idling pressure in the high-pressure channel 7, which can also be called "stand-by pressure" or "margin pressure". This enables energy-saving operation.
As can be seen from the schematic view, the arrangement of the lines and the location of the individual elements in the pre-compensated valve modules 3, 5 is substantially the same as the corresponding arrangement of the lines and locations of the elements in the post-compensated valve modules 4, 6. This applies, as can be seen clearly, for the path from the directional valve 15 to the work connections A, B, including the non-return valves 23, 24 that can be opened.
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-12 -The location of the compensation valves 19, 28, however, is the same in both valve module kinds. Merely the closing spring 26 of the compensation slide 25 must be moved to the other side of the compensation slide 25 to make a pre-compensated compensation slide 20. Further, it is merely required to remove the line existing between the compensation slide 25 and the load-sensing line 13 and to replace it by a line between the inlet 17 of the directional valve 15 and the compensation slide 20. In principle, it is therefore sufficient to provide corresponding bores in the housing for both of these lines and then close those bores by means of plugs or the like. (

Claims (8)

  1. -13 -C L A I M S: 1. A hydraulic valve arrangement comprising a
    plurality of valve modules, each valve module having a supply channel arrangement comprising a high-pressure channel and a low-pressure channel, a work connection arrangement with at least one work connection, a directional valve arrangement between the supply channel arrangement and the work connection arrangement, and a compensation arrangement, wherein, in at least one valve module, the compensation arranement is a pre-cornpensation arrangement and, in at least one other valve module, the compensation arrangement is a post-compensation arrangement.
  2. 2. A valve arrangement according to claim 1, wherein the post-compensation arrangement has a closing spring and the pre-compensation arrangement has an opening spring, the closing spring being weaker than the opening spring.
  3. 3. A valve arrangement according to claim 2, wherein the opening spring generates a control force smaller than the pressure force during idling acting against the opening spring.
  4. 4. A valve arrangement according to any one of claims 1 to 3, wherein, in the valve module with the pre-compensation arrangement, the compensation arrangement is located in a line that runs from an ( -14 -outlet to an inlet of the directional valve arrangement.
  5. 5. A valve arrangement according to claim 4, wherein both the pre-compensation arrangement and the post-compensation arrangement are located in lines running from an outlet to an inlet of the directional valve arrangement.
  6. 6. A valve arrangement according to claim 5, wherein the compensation arrangements are located in the same position in both the valve module(s) with pre-compensation arrangements and in the valve module(s) with post-compensation arrangements.
  7. 7. A valve arrangement according to any one of claims 1 to 6, wherein both the valve module(s) with pre-compensation arrangement and the valve module(s) with post-compensation arrangement have similar valve housings, and a spring of the pre-compensation arrangement is located at a different side of a slide from a spring of the post-compensation arrangement.
  8. 8. A hydraulic valve arrangement substantially as herein described with reference to, and as illustrated by, the single figure of the accompanying drawing.
GB0724634A 2006-12-20 2007-12-18 Hydraulic valve arrangement Withdrawn GB2445094A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610060326 DE102006060326B4 (en) 2006-12-20 2006-12-20 Hydraulic valve arrangement

Publications (2)

Publication Number Publication Date
GB0724634D0 GB0724634D0 (en) 2008-01-30
GB2445094A true GB2445094A (en) 2008-06-25

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ID=39048262

Family Applications (1)

Application Number Title Priority Date Filing Date
GB0724634A Withdrawn GB2445094A (en) 2006-12-20 2007-12-18 Hydraulic valve arrangement

Country Status (10)

Country Link
US (1) US7770596B2 (en)
CN (2) CN101255881A (en)
AU (1) AU2007249079A1 (en)
BR (1) BRPI0704683A (en)
DE (1) DE102006060326B4 (en)
FR (1) FR2910566A1 (en)
GB (1) GB2445094A (en)
IT (1) ITTO20070913A1 (en)
RU (1) RU2353823C1 (en)
ZA (1) ZA200710749B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20100359A1 (en) * 2010-06-08 2011-12-09 Hydrocontrol S P A Con Unico Socio HYDRAULIC PLANT AND HYDRAULIC DISTRIBUTOR FOR THE OPERATION OF OPERATING MACHINES
ITBO20100358A1 (en) * 2010-06-08 2011-12-09 Hydrocontrol S P A Con Unico Socio HYDRAULIC PLANT AND HYDRAULIC DISTRIBUTOR FOR THE OPERATION OF OPERATING MACHINES

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE471459T1 (en) * 2004-12-15 2010-07-15 Actuant Corp DIRECT ACTING, NEUTRAL 4-WAY, 3-POSITION TANDEM CENTER VALVE
WO2011115647A1 (en) 2010-03-17 2011-09-22 Parker Hannifin Corporation Hydraulic valve with pressure limiter
WO2013049573A2 (en) 2011-09-30 2013-04-04 Eaton Corporation Pre- and post - compensational valve arrangement
CN102734246B (en) * 2012-07-13 2016-01-20 三一汽车制造有限公司 Hydrovalve and pressure compensating method, hydraulic valve bank, hydraulic system and engineering machinery
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FR2910566A1 (en) 2008-06-27
US20080224073A1 (en) 2008-09-18
BRPI0704683A (en) 2008-08-19
AU2007249079A1 (en) 2008-07-10
DE102006060326B4 (en) 2008-11-27
CN104214153A (en) 2014-12-17
ITTO20070913A1 (en) 2008-06-21
GB0724634D0 (en) 2008-01-30
ZA200710749B (en) 2008-09-25
DE102006060326A1 (en) 2008-07-03
US7770596B2 (en) 2010-08-10
CN101255881A (en) 2008-09-03

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